CN106414900B - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- CN106414900B CN106414900B CN201580026527.4A CN201580026527A CN106414900B CN 106414900 B CN106414900 B CN 106414900B CN 201580026527 A CN201580026527 A CN 201580026527A CN 106414900 B CN106414900 B CN 106414900B
- Authority
- CN
- China
- Prior art keywords
- drive shaft
- scroll compressor
- bearing
- lubrication
- scroll
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
- F04C18/0223—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
Abstract
Scroll compressor (1) includes that orbitting scroll arrangement (7) and being configured to drives orbitting scroll arrangement (7) to carry out the drive shaft (18) of moving movement, and drive shaft (18) includes lubrication channel (32) and is fluidly connected to lubrication channel (32) and appears in the first lubrication hole (35) in the outer walls of drive shaft (18).Scroll compressor (1) further includes the rotation axis axial dipole field and respective the first and second bearings (38,39) for being configured to engage with drive shaft (18) along drive shaft (18).First and second bearings (38,39) and drive shaft (18) locally limit first annular gap (44), and the first lubrication hole (35) appears in first annular gap.First bearing (38) and drive shaft (18) limit the first oil pocket for being fluidly connected to first annular gap (44), and second bearing (39) and drive shaft (18) limit the second oil pocket for being fluidly connected to first annular gap (44).
Description
Technical field
The present invention relates to a kind of scroll compressors, and more particularly to a kind of swirl type cold compressor.
Background technique
As it is known, scroll compressor may include:
Closed container,
Compression unit, the compression unit are configured for compression refrigerant and including fixed scrolls and moving whirlpool
Capstan,
Drive shaft, the drive shaft are configured for that the orbitting scroll is driven to carry out moving movement, and the drive shaft is especially
Include:
Lubrication channel, the lubrication channel are configured to by being able to fuel feeding from oil storage tank by the shaft-driven oil pump of the driving,
The lubrication channel extends at least part of the length of the drive shaft, and
Multiple lubrication holes, these lubrication holes and the lubrication channel fluidly connect and appear in the outer wall of the drive shaft
In, these lubrication holes along the drive shaft rotation axis axial dipole field,
Driving unit, the driving unit are coupled to the drive shaft and are arranged to drive the drive shaft around rotary shaft
Line rotation, and
Multiple bearings, these bearings along the drive shaft rotation axis axial dipole field and respectively be configured to should
Drive shaft engagement.
In the drive shaft rotary course, the oil pump be the lubrication channel fuel feeding, and then by centrifugal force and via
The oil supplied is fed into the supporting surface of these bearings by these lubrication holes, this causes to be lubricated these bearings.
In order to ensure satisfactorily being lubricated bearing, drive shaft is equipped with a profit preferably in front of each bearing
Slide opening, and each lubrication hole occurs preferably on lubrication channel, opposite with the rotation axis of drive shaft inner wall part, makes
The oil supplied in lubrication channel is obtained to flow by centrifugal action along the inner wall part and readily enter by centrifugal force
Lubrication hole.
However, the final angle position of lubrication hole depends on applying between drive shaft and bearing in drive shaft rotary course
The angle position of the radial load added.In fact, if the radial direction that lubrication hole is located at and applies between drive shaft and bearing is born
The identical angular position in the angle position of load, the then pressure that the radial load generates at each lubrication hole will prevent oil
It is flowed out from corresponding lubrication hole, this will hinder satisfactorily to lubricate bearing.
It is thus impossible to abide by appropriate angle position of the lubrication hole relative to the inner wall part of lubrication channel always, this will
Lead to the reduction of bearing lubrication quality.
Further, since the angle position of the radial load applied between drive shaft and bearing depends on driving axle speed
Degree, so using variable speed electric motors, particularly that may make it difficult to select to be most suitable for lubrication hole as driving unit other than service condition
Angle position.
Summary of the invention
The object of the present invention is to provide the systems of improved the shortcomings that traditional scroll compressor can be overcome encountered a kind of
Cold compressor.
It is a further object of the present invention to provide the scroll compressors that one kind can lubricate its driving shaft bearing in an optimal manner
Machine.
According to the present invention, this scroll compressor includes at least:
Compression unit, the compression unit are configured for compression refrigerant and include at least the first fixed scroll
With orbitting scroll arrangement,
Drive shaft, the drive shaft are configured for that the orbitting scroll arrangement is driven to carry out moving movement, the drive shaft
It includes at least:
Lubrication channel, the lubrication channel be configured to be able to from oil storage tank fuel feeding and the length of the drive shaft to
Extend in few a part, and
- the first lubrication hole, first lubrication hole are fluidly connected to the lubrication channel and appear in the outer wall of the drive shaft
In,
Driving unit, the driving unit are coupled to the drive shaft and are arranged to drive the drive shaft around rotary shaft
Line rotation, and
- the first and second bearings, first and second bearing along the drive shaft the rotation axis axial dipole field and
Respectively it is configured to engage with the drive shaft,
Wherein, first and second bearing and the drive shaft at least locally limit first annular gap, first lubrication
Hole appears in the first annular gap, the first bearing and the drive shaft define therebetween be fluidly connected to this it is first annular between
First oil pocket of gap, and the second bearing and the drive shaft define therebetween and are fluidly connected to the second of the first annular gap
Oil pocket.
In the drive shaft rotary course, the oil into the lubrication channel is at least partly supplied via first lubrication hole
The first annular gap is given, and subsequently enters first and second oil pocket.These supplies ensure the first and second bearings
Best lubrication, regardless of the angle of the first lubrication hole and the radial load applied between drive shaft and first and second bearing
How is position, and the revolving speed regardless of the drive shaft.
Further, which keeps pressurization oil close to first and second bearing, this is avoided or is limited
Bearing decompression, that is, bearing oil is disposed by refrigerant.
In addition, the configuration of the drive shaft and first and second bearing ensures the best lubrication of the first and second bearings,
Even if oil is supplied to lubrication channel by centrifugal pump.This makes screw compressor less expensive.
According to an embodiment of the invention, the drive shaft further include it is substantially flat and respectively for this first and second
First and second outer surface portions of bearing (that is, along its extension), first outer surface portion and the first bearing limit this first
Oil pocket, and second outer surface portion and the second bearing limit second oil pocket.
According to an embodiment of the invention, first and second outer surface portion is arranged essentially parallel to the rotation axis of the drive shaft
Extend.
According to an embodiment of the invention, the drive shaft includes to form first and second outer surface portion first flat outer
Portion, the first flat outside further extend along the first annular gap.
According to an embodiment of the invention, the rotation axis that the first flat outside is arranged essentially parallel to the drive shaft prolongs
It stretches.
According to an embodiment of the invention, at least one of first lubrication hole and first and second outer surface portion about
The rotation axis of the drive shaft deviates in angle.
According to an embodiment of the invention, first lubrication hole appear in the drive shaft, exist with the first flat outside
In the outside deviated in angle.
According to an embodiment of the invention, first lubrication hole and first and second outer surface portion are being parallel to the drive shaft
Rotation axis direction on substantial alignment.
According to an embodiment of the invention, first lubrication hole appears on the first flat outside.
According to an embodiment of the invention, the rotational axis offset of the lubrication channel and the drive shaft, which goes out
The the first present lubrication channel, opposite about the longitudinal axis of the lubrication channel and the rotation axis of drive shaft inner wall part
On, and more precisely, appear in the lubrication channel, in the drive shaft rotary course oil by centrifugal action along it
On first inner wall part of flowing.
It is revolved according to an embodiment of the invention, the first flat outside is located substantially in terms of angle in the drive shaft
The angle position that the angle position of radial load that applies between the drive shaft and first and second bearing is opposite during turning
Place is set,
According to an embodiment of the invention, first and second bearing is respectively configured to also engage first fixed scroll
One of with the orbitting scroll arrangement.
In other words, each bearing setting in first and second bearing in the drive shaft and first fixed scroll and
In orbitting scroll arrangement between one.
According to an embodiment of the invention, first lubrication hole generally radially prolongs relative to the rotation axis of the drive shaft
It stretches.
According to an embodiment of the invention, the screw compressor further includes the third and fourth bearing, third and fourth bearing
Along the drive shaft rotation axis axial dipole field and be respectively configured to engage with the drive shaft, third and fourth bearing
And the drive shaft at least locally limits the second annular gap, and wherein, which further includes the second lubrication hole, this second
Lubrication hole is fluidly connected to the lubrication channel and appears in second annular gap.
According to an embodiment of the invention, the 3rd bearing and the driving axis limit are fluidly connected to second annular gap
Third oil pocket, and the fourth bearing and the driving axis limit are fluidly connected to the 4th oil pocket of second annular gap.
According to an embodiment of the invention, the drive shaft further include it is substantially flat and respectively for this third and fourth
Third and fourth outer surface portion of bearing, the third outer surface portion and the 3rd bearing limit the third oil pocket, and the 4th
Outer surface portion and the fourth bearing limit the 4th oil pocket.
According to an embodiment of the invention, third and fourth bearing is respectively configured to also engage first fixed scroll
The other of with the orbitting scroll arrangement.
According to an embodiment of the invention, the drive shaft includes at least driving portion and first by guide portion, which is matched
It is set to for driving the orbitting scroll arrangement to carry out moving movement.
According to an embodiment of the invention, first and second bearing is arranged to for rotatably guiding and supporting the drive
The first of moving axis is by guide portion.
According to an embodiment of the invention, the drive shaft further includes second by guide portion, this is first and second by guidance position
In the two sides of the driving portion.
According to an embodiment of the invention, third and fourth bearing is arranged to engage with the driving portion of the drive shaft.
According to an embodiment of the invention, the drive shaft extends across the orbitting scroll arrangement so that this first and second
The two sides of the orbitting scroll arrangement are located at by guide portion.
According to an embodiment of the invention, the drive shaft further includes third lubrication hole, which is fluidly connected to this
Lubrication channel and the second of the drive shaft is appeared in by the outer wall of guide portion.
According to an embodiment of the invention, the drive shaft further includes first end and the second end opposite with the first end
Portion, the first end include the outer diameter that concavity and the outer diameter that has are greater than the second end.The first end of the drive shaft
This arrangement in portion improves the rigidity of the drive shaft, the flexure without increasing the drive shaft.When the drive shaft is more rigid,
Its first intrinsic frequency translation is to higher level.
According to an embodiment of the invention, the concavity appears on the end face of the first end of the drive shaft.
According to an embodiment of the invention, the outer diameter of the first end corresponds to the maximum outside diameter of the drive shaft, and this
The outer diameter of two ends corresponds to the minimum outer diameter of the drive shaft.
According to an embodiment of the invention, the driving unit includes motor, which has stator and rotor, rotor assembly
On the first end of the drive shaft.
According to an embodiment of the invention, the drive shaft further include be fluidly connected to the lubrication channel at least one ventilation it is logical
Road.The degassing for being present to ensure that the oil recycled in the lubrication channel of the vent passages, and will especially be originated from degassing
Except discharge refrigerant to the drive shaft.Such degassing prevents refrigerant from bearing lubrication being made to degenerate.
According to an embodiment of the invention, the vent passages include the flow section for being configured to limit about the vent passages
Restricted zone.The restricted zone prevents or limitation is discharged by the oil of the vent passages or oil leakage, even if when in lubrication channel
Oil mass it is especially big and especially in the drive shaft high speed rotation.This supply improves compressor efficiency.
According to an embodiment of the invention, the restricted zone is configured for radially constraining the flow section of the vent passages.
According to an embodiment of the invention, the restricted zone is configured so that, and at the restricted zone, the flowing of the vent passages
The width in section is less than the height of the flow section of the vent passages.The configuration limitation of the restricted zone passes through the vent passages
Oil discharge, while ensure it is appropriate oil degassing.
According to an embodiment of the invention, the restricted zone is located near the inner wall part of the lubrication channel.
According to an embodiment of the invention, the restricted zone is substantially centered on the rotation axis of the drive shaft.
According to an embodiment of the invention, the vent passages include at least the rotation axis substantially diameter relative to the drive shaft
The first ventilation unit extended to ground, the restricted zone are arranged on first ventilation unit.The configuration of the vent passages keeps oil de-
Gas becomes easy.
According to an embodiment of the invention, first ventilation unit includes the first section and the setting that the restricted zone upstream is arranged in
The second section in the restricted zone downstream.
According to an embodiment of the invention, the vent passages include the second ventilation unit, second vent locations are first logical in this
Wind subordinate swims and is arranged essentially parallel to the rotation axis extension of the drive shaft.
According to an embodiment of the invention, second ventilation unit substantially leads to the lubrication about the rotation axis of the drive shaft
First inner wall part (that is, inner wall part that oil is flowed by centrifugal action along it in the drive shaft rotary course) in road is on the contrary
Positioning.
According to an embodiment of the invention, the vent passages appear in the lubrication channel, rotary shaft positioned at the drive shaft
In the second inner wall part near line.
In other words, the vent passages appear in the lubrication channel, towards the drive shaft rotation axis turn to second in
In wall portion.
According to an embodiment of the invention, the vent passages are fluidly connected to the concavity of the first end of the drive shaft.
According to an embodiment of the invention, the drive shaft further includes the closure for being configured for part and limiting the vent passages
Component.
According to an embodiment of the invention, the enclosed member is configured to turn off the end of the lubrication channel.
According to an embodiment of the invention, the enclosed member includes the limitation structure for being configured for part and limiting the restricted zone
Part.
According to an embodiment of the invention, the enclosed member includes the ventilation hole that at least part limits the vent passages.For example,
The ventilation hole can form the second ventilation unit of vent passages.
According to an embodiment of the invention, the ventilation hole appears in the concavity of the first end of the drive shaft.
According to an embodiment of the invention, the lubrication channel is arranged essentially parallel to the rotation axis of the drive shaft.
According to an embodiment of the invention, the lubrication channel is stepped and including first passage portion and second channel
Portion, the first passage portion are configured to be able to fuel feeding from the oil storage tank, and it is first logical that the internal diameter which has is greater than this
The internal diameter in road portion.
According to an embodiment of the invention, the lubrication channel is arranged to and oil pump shaft-driven by the driving from the storage
Oil groove is able to fuel feeding.
According to an embodiment of the invention, first fixed scroll includes the first fixed helical wrap, and the moving
Scroll plate arrangement includes the first moving helical wrap, and the first fixed helical wrap and the first moving spiral winding
Part forms multiple first discharge chambes.
According to an embodiment of the invention, the compressor unit further includes the second fixed scroll, second fixed scroll
Including the second fixed helical wrap, and first and second fixed scroll limits internal capacity, orbitting scroll peace
Row is arranged in the internal capacity and further includes the second moving helical wrap, the second fixed helical wrap and this second
Moving helical wrap forms multiple second discharge chambes.
According to an embodiment of the invention, the first and second movings helical wrap is separately positioned on the first of common substrate
On face and the second face, second face is opposite with first face.
According to an embodiment of the invention, the scroll compressor also includes at least 5th bearing, which is configured
At the engagement drive shaft and second fixed scroll.
According to an embodiment of the invention, the 5th bearing is configured for rotatably guiding and supporting the drive shaft
First by guide portion.
According to an embodiment of the invention, the scroll compressor further includes the first counterweight and second for being connected to the drive shaft
Counterweight, first and second counterweight are located on the two sides of the orbitting scroll arrangement.First counterweight and the second counterweight
This mass balance for arranging to allow the orbitting scroll arrangement, wherein the inclination of the drive shaft is limited.The drive shaft
This finite inclination improves the reliability of these bearings and the reliability of the driving unit, and therefore improves the compressor
Reliability and performance.
According to an embodiment of the invention, the scroll compressor is vertical vortex, and the drive shaft is substantially
Vertically extend.
According to an embodiment of the invention, the drive shaft is staged drive shaft.The arrangement ensures easy assembling whirlpools
Rotary compressor.According to an embodiment of the invention, the staged drive shaft includes at least four different diameters, in order to compress
The assembling of machine, and limit the deformation under the lower shaft flexing of high speed/sustain at a high speed.
According to an embodiment of the invention, the scroll compressor is variable speed scroll formula compressor.
According to another embodiment of the invention, which is constant speed scroll compressor.
In view of the attached drawing for three embodiments for indicating scroll compressor according to the present invention as non-limiting examples, lead to
Cross the following explanation of reading, these and other the advantages of will be apparent.
Detailed description of the invention
When read in conjunction with the accompanying drawings, the following detailed description of one embodiment of the present of invention will be better understood, so
And, it will be appreciated that the present invention is not limited to disclosed specific embodiments.
Fig. 1 is the longitudinal sectional view of the scroll compressor of first embodiment according to the present invention.
Fig. 2 and Fig. 3 is the perspective view of the drive shaft of the screw compressor of Fig. 1.
Fig. 4 is the longitudinal sectional view of the drive shaft of Fig. 2.
Fig. 5 to Fig. 8 be the drive shaft of Fig. 2, respectively along plane V-V, VI-VI, VII-VII, VIII-VIII of Fig. 4 cut
Disconnected local perspective view.
Fig. 9 is the drive shaft of Fig. 2, plane truncation along longitudinal direction local perspective view.
Figure 10 is the drive shaft of Fig. 2, transversely plane truncation local perspective view.
Figure 11 is the longitudinal sectional view of the drive shaft of the scroll compressor of second embodiment according to the present invention.
Figure 12 is the longitudinal sectional view of the drive shaft of the scroll compressor of third embodiment according to the present invention.
Specific embodiment
Fig. 1 shows the scroll compressor 1 for occupying vertical position.
Scroll compressor 1 includes closed container 2 and is arranged in closed container 2 and is configured for compression refrigeration
The compression unit 3 of agent.
Compression unit 3 includes the first and second fixed scrolls 4,5 for defining internal capacity 6.In particular, first He
Second fixed scroll 4,5 is fixed relative to the closed container 2.For example, first fixed scroll 4 can be secured to
On second fixed scroll 5.Compression unit 3 further includes that the orbitting scroll being arranged in internal capacity 6 arranges 7.
First fixed scroll 4 includes substrate 8 and the spiral stretched out from the substrate 8 towards second fixed scroll 5
Wrap 9, and the second fixed scroll 5 includes substrate 11 and stretches out from the substrate 11 towards first fixed scroll 4
Helical wrap 12.
The orbitting scroll arrangement 7 is stretched including substrate 13, from the first of the substrate 13 facing towards first fixed scroll 4
The first helical wrap 14 out and the second the second spiral shell stretched out facing towards second fixed scroll 5 from the substrate 13
Wrap 15 is revolved, second face is with first face on the contrary, stretching first and second helical wrap 14,15 in opposite direction
Out.First and second fixed scrolls 4,5 are located at orbitting scroll and arrange above and below in the of 7.
Orbitting scroll arranges 7 the first helical wrap 14 and the helical wrap 9 of the first fixed scroll 4 to match
It closes, to form multiple discharge chambes 16 between them, and orbitting scroll arranges 7 the second helical wrap 15 and second solid
The helical wrap 12 of determine vortex disk 5 matches, to form multiple discharge chambes 17 between them.Each discharge chambe 16,17
With variable volume, when orbitting scroll arrangement 7 be driven and when relative to the first and second fixed scrolls 4,5 moving,
The variable volume reduces from outside towards inside.
In addition, scroll compressor 1 includes staged drive shaft 18 and driving unit 19, which is configured
At for driving orbitting scroll to arrange the movement of 7 movings, which is connected to drive shaft 18 and is configured for driving
Dynamic drive shaft 18 is rotated around rotation axis.Driving unit 19 includes the motor positioned at 4 top of the first fixed scroll.This is electronic
The stator 22 that machine has the rotor 21 being assemblied in drive shaft 18 and arranges around rotor 21.For example, the motor can be change
Electric motor with speed.
Drive shaft 18 extends vertically through the substrate 13 that orbitting scroll arranges 7.Drive shaft 18 includes first end 23
With the second end 24, which is located at the top of the first fixed scroll 4 and rotor 21 is assembled in the first end
On, and the second end is opposite with first end 23 and is located at the lower section of the second fixed scroll 5.What first end 23 had
Outer diameter is greater than the outer diameter of the second end 24.First end 23 includes concavity 25, which appears in first end 23
, in opposite with the second end 24 end face.
Drive shaft 18 further includes first being guided by guide portion 26 and second between first and second end 23,24
Portion 27 and positioned at this first and second it is off-centered partially by the rotation axis A between guide portion 26,27 and from drive shaft 18
Heart driving portion 28.Eccentric drive portion 28 is arranged to arrange 7 cooperations with orbitting scroll, to cause when operating the motor
The orbitting scroll arrangement is driven and does moving movement relative to the first and second fixed scrolls 4,5.
Drive shaft 18 further include the first flat outside 29 extended along first by the outer surface of guide portion 26 and along
The second flat outside 31 that the outer surface in eccentric drive portion 28 extends.Advantageously, the first and second flat outsides 29,31 bases
Extend in sheet perpendicular to the rotation axis A of drive shaft 18.First and second flat outsides 29,31 each other can be relative to driving
The rotation axis A of axis 18 is deviated in terms of angle, and such as mutually substantially diametrically opposite.
Drive shaft 18 further includes lubrication channel 32, the lubrication channel extend in a part of the length of drive shaft 18 and
The oil pump 34 by being driven by the second end 24 of drive shaft 18 is arranged to be able to from the oil storage tank limited by closed container 2
Fuel feeding.
According to Fig. 1 to first embodiment shown in Fig. 10, lubrication channel 32 is arranged essentially parallel to the rotary shaft of drive shaft 18
Line A and from the rotation axis A of drive shaft 18 deviate, i.e., deviation center.However, according to another embodiment of the invention, profit
Slide-through road 32 can be tilted relative to the rotation axis A of drive shaft 18.
According to Fig. 1 to first embodiment shown in Fig. 10, oil pump 34 is made of pump element and end, which, which has, connects
It is connected to the second end 24 of drive shaft 18, substantially cylindrical interconnecting piece, which has curved shape and be equipped with
There is hydraulic fluid port.However, according to another embodiment of the invention, oil pump 34 can be made of the second end 24 of drive shaft 18.
Drive shaft 18 further includes being fluidly connected to lubrication channel 32 and appearing in the first of drive shaft 18 by guide portion 26
Outer wall in lubrication hole 35, the eccentric drive portion 28 for being fluidly connected to lubrication channel 32 and drive shaft 18 occur outer wall in
Lubrication hole 36 and be fluidly connected to lubrication channel 32 and appear in the second outer wall by guide portion 27 of drive shaft 18
Lubrication hole 37.Advantageously, each lubrication hole is generally radially extending both relative to the rotation axis A of drive shaft 18.
Scroll compressor 1 further includes the multiple bearing elements for being configured to engage drive shaft 18.These bearing element packets
It includes and is respectively disposed at the first of the first fixed scroll 4 and drive shaft 18 by two fixing bearings 38,39 between guide portion 26,
Two between orbitting scroll arrangement 7 and the eccentric drive portion 28 of drive shaft 18 are respectively disposed at around dynamic bearing 41,42, and
It is arranged in the second of the second fixed scroll 5 and drive shaft 18 by a fixing bearing 43 between guide portion 27.It should be noted that
Bearing 38,39,41,42,43 is located on the same side of drive shaft 18 relative to first end 23.
Fixing bearing 38,39, drive shaft 18 and the first fixed scroll 4 limit first annular gap 44, and lubrication hole 35 goes out
In the present first annular gap.Further, first along drive shaft 18 is extended by guide portion 26 first flat outer
Portion 29 includes the first outer surface portion 29a extended along fixing bearing 38 and the second outer surface portion extended along fixing bearing 39
29b.First outer surface portion 29a and fixing bearing 38 limit the first oil pocket 45 for being fluidly connected to first annular gap 44, and
Second outer surface portion 29b and fixing bearing 39 limit the second oil pocket 46 for being fluidly connected to first annular gap 44.
Around dynamic bearing 41,42, second annular gap 47 of drive shaft 18 and the restriction of the second fixed scroll 5.Further, edge
Drive shaft 18 eccentric drive portion 28 extend the second flat outside 31 include along outside the third that dynamic bearing 41 extends
Surface element 31a and along the 4th outer surface portion 31b extended around dynamic bearing 42.Third outer surface portion 31a and around dynamic bearing 41 limit
Surely it is fluidly connected to the third oil pocket 48 of the second annular gap 47, and third outer surface portion 31b and limiting around dynamic bearing 42 flows
Body connects the 4th oil pocket 49 that the second annular gap 47 is arrived.
According to Fig. 1 to first embodiment shown in Fig. 10, lubrication hole 35 appears in the first of drive shaft 18 by guide portion 26
Outside on, angularly offset from outside this about the rotation axis A of drive shaft 18 and the first flat outside 29, and lubricate
Hole 36 appears on the second flat outside 31.
Drive shaft 18 further includes on the one hand being fluidly connected on lubrication channel 32 and being on the other hand fluidly connected to drive
Vent passages 51 on the concavity 25 of the first end 23 of axis 18.
As Fig. 9 more preferably shown in, vent passages 51 include relative to drive shaft 18 rotation axis A it is generally radially extending
The first ventilation unit 51a and positioned at the first downstream ventilation unit 51a and be arranged essentially parallel to the rotation axis A of drive shaft 18 and prolong
The the second ventilation unit 51b stretched.First embodiment according to the present invention, the first ventilation unit 51a appear in being located at for lubrication channel 32
On inner wall part near the rotation axis A of drive shaft 18, and the second ventilation unit 51b about drive shaft 18 rotation axis A with
Lubrication channel 32 is opposite.The position of second ventilation unit 51b is advantageously with lubrication channel 32, oil in 18 rotary course of drive shaft
It is opposite along the inner wall part of its flowing by centrifugal action.
Vent passages 51 further include being arranged on the first ventilation unit 51a and being configured to radially limit the first ventilation unit
The restricted zone 52 of the flow section of 51a.First ventilation unit 51a may include that the first part of 52 upstream of restricted zone is arranged in and sets
Set the second part in 52 downstream of restricted zone.Further, restricted zone 52 can be located near the inner wall part of lubrication channel 32.Root
According to the embodiment of the present invention, restricted zone can be by 52 substantially centered on the rotation axis A of the drive shaft.
Advantageously, restricted zone 52 is configured so that, at restricted zone 52, the width of the flow section of the first ventilation unit 51a
Spend height H of the W less than the flow section of the first ventilation unit 51a.
Drive shaft 18 further includes enclosed member 53, the enclosed member be located in the concavity 25 of first end 23 and by
It is disposed for closing the end of lubrication channel 32 and locally limits vent passages 51.
Enclosed member 53 includes being configured for part to limit the limiting member 54 of restricted zone 52 and form vent passages
The ventilation hole 55 of 51 the second ventilation unit 51b.
Scroll compressor 1 further includes the first counterweight 56 and the second counterweight 57, first counterweight and this second with reconnection
To drive shaft 18 and it is arranged to balance the quality of orbitting scroll arrangement 7.First counterweight 56 is located at the first fixed scroll 4
Top, and the second counterweight 57 is located at the lower section of the second fixed scroll 5.
According to Fig. 1 to first embodiment shown in Fig. 10, the first counterweight 56 and drive shaft 18 are formed as single type element, and
And second counterweight 57 be different from drive shaft 18 and be attached to this dynamic driving on axis.For example, the first counterweight 56 can be by from drive
Material is removed on moving axis 18 to be formed.
Scroll compressor 1 further include refrigerant suction port (being not shown in these figures) and outlet (in these figures
It is not shown), which is connected to interior room 6, refrigerant is supplied to compression unit 3 to realize, which is used for
The refrigerant of compression is discharged to except scroll compressor 1.
At runtime, oil pump 34 be supplied to the oil of lubrication channel 32 by centrifugal action along lubrication channel 32, with drive
The rotation axis A of moving axis 18 opposite inner wall part flowing.It is supplied to the first part of the oil of lubrication channel 32 to enter lubrication hole 37
And lubricate fixing bearing 43.It is supplied to the second part of the oil of lubrication channel 32 to enter lubrication hole 36 and the third and fourth oil
Chamber 48,49, and then lubricate around dynamic bearing 41,42.It is supplied to the Part III of the oil of lubrication channel 32 to subsequently enter lubrication
Hole 35, first annular gap 44 and the first and second oil pockets 45,46, and then lubricate fixing bearing 38,39.
Further, vent passages 51 ensure the degassing of the oil recycled in lubrication channel 32, and especially by source
From except the discharge refrigerant to drive shaft 18 of degassing.Restricted zone 52 prevent or at least limit vent passages 51 oil discharge or
Oil leakage, even if when the oil mass in lubrication channel 32 is especially big.
Figure 11 indicates the drive shaft 18 of the scroll compressor 1 of second embodiment according to the present invention, the second embodiment
With first embodiment the difference is that drive shaft 18 includes respectively appearing in the first and second of the first flat outside 29
Two lubrication holes 35 in outer surface portion 29a, 29b and appear in the only one lubrication hole 36 in the second annular gap 47.According to
The second embodiment of the invention, lubrication hole 36 can appear on the outside in eccentric drive portion 28 of drive shaft 18, this is outer
Portion is angularly offset from about the rotation axis A of drive shaft 18 with the second flat outside 31.
Figure 12 indicates the drive shaft 18 of the scroll compressor 1 of third embodiment according to the present invention, the 3rd embodiment
With first embodiment the difference is that drive shaft 18 includes the only one lubrication hole 36 appeared in the second annular gap 47.
Second embodiment according to the present invention, lubrication hole 36 can appear on the outside in eccentric drive portion 28 of drive shaft 18,
It is angularly offset from outside this about the rotation axis A of drive shaft 18 and the second flat outside 31.
Certainly, the embodiment that the present invention is not limited to be described above by means of non-limiting example, on the contrary, it covers its institute
There is embodiment.
Claims (15)
1. a kind of scroll compressor (1), includes at least:
Compression unit (3), the compression unit are configured for compression refrigerant and include at least the first fixed scroll
(4) and orbitting scroll arrangement (7),
Drive shaft (18), the drive shaft are configured for that the orbitting scroll arrangement (7) is driven to carry out moving movement, the drive
Moving axis (18) includes at least:
Lubrication channel (32), the lubrication channel are configured to be able to fuel feeding from oil storage tank and in the length of the drive shaft (18)
At least part on extend, and
- the first lubrication hole (35), first lubrication hole are fluidly connected to the lubrication channel (32) and appear in the drive shaft
(18) in outer wall,
Driving unit, the driving unit are connected to the drive shaft (18) and are arranged to drive the drive shaft (18) around rotation
Axis (A) rotation,
- the first and second bearings (38,39), first and second bearing are axially inclined along the rotation axis of the drive shaft (18)
It moves and is respectively configured to engage with the drive shaft (18),
Wherein, first and second bearing (38,39) and the drive shaft (18) at least part limit first annular gap (44),
First lubrication hole (35) appears in the first annular gap (44), and the first bearing (38) and the drive shaft (18) limit stream
Body is connected to the first oil pocket (45) of the first annular gap (44), and the second bearing (39) and the drive shaft (18) limit
It is fluidly connected to the second oil pocket (46) of the first annular gap (44).
2. scroll compressor (1) according to claim 1, wherein the drive shaft (18) further includes substantially flat
And respectively for the first and second outer surface portions (29a, 29b) of first and second bearing (38,39), first outer surface
Portion (29a) and the first bearing (38) limit first oil pocket (45), and second outer surface portion (29b) and the second bearing
(39) second oil pocket (46) is limited.
3. scroll compressor (1) according to claim 2, wherein the drive shaft (18) include formed this first and the
The flat outside (29) of the first of two outer surface portions (29a, 29b), the first flat outside (29) is along this first annular
Gap (44) further extends.
4. scroll compressor (1) according to claim 2 or 3, wherein first lubrication hole (35) and this first and the
At least one of two outer surface portions (29a, 29b) deviate in angle about the rotation axis of the drive shaft (18).
5. scroll compressor (1) according to claim 2 or 3, wherein first lubrication hole (35) and this first and the
Two outer surface portions (29a, 29b) substantial alignment on the direction of the rotation axis for being parallel to the drive shaft (18).
6. scroll compressor (1) according to claim 1, wherein the lubrication channel (32) and the drive shaft (18)
The rotational axis offset, first lubrication hole (35) appear in rotary shaft with the drive shaft (18) of the lubrication channel (32)
On the first opposite inner wall part of line.
7. scroll compressor (1) according to claim 1, wherein first and second bearing (38,39) is respectively matched
It is set to and also engages one of first fixed scroll (4) and the orbitting scroll arrangement (7).
8. scroll compressor (1) according to claim 1, wherein the drive shaft (18) further includes being fluidly connected to this
The vent passages (51) of lubrication channel (32).
9. scroll compressor (1) according to claim 8, wherein the vent passages (51) include being configured for
Limit the restricted zone (52) of the flow section of the vent passages (51).
10. scroll compressor (1) according to claim 9, wherein the restricted zone (52) is configured so that, at this
At restricted zone, the width of the flow section of the vent passages (51) is less than the height of the flow section of the vent passages (51).
11. scroll compressor (1) according to claim 9 or 10, wherein the vent passages (51) include at least opposite
In the first ventilation unit (51a) that the rotation axis (A) of the drive shaft (18) essentially radially extends, the restricted zone (52) setting
On first ventilation unit (51a).
12. scroll compressor (1) according to claim 11, wherein the vent passages (51) include the second ventilation unit
(51b), second vent locations are in the first ventilation unit downstream (51a) and are arranged essentially parallel to the rotation of the drive shaft (18)
Shaft axis extends.
13. scroll compressor (1) according to claim 8, wherein the vent passages (51) appear in the lubrication channel
(32), be located at the drive shaft (18) the rotation axis near the second inner wall part on.
14. scroll compressor (1) according to claim 9, wherein the drive shaft (18) further includes being configured for
Part limits the enclosed member (53) of the vent passages (51).
15. scroll compressor (1) according to claim 14, wherein the enclosed member (53) includes being configured to use
In the limiting member (54) for locally limiting the restricted zone (52).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR14/54427 | 2014-05-16 | ||
| FR1454427A FR3021075B1 (en) | 2014-05-16 | 2014-05-16 | SPIRAL COMPRESSOR |
| PCT/EP2015/051549 WO2015172895A1 (en) | 2014-05-16 | 2015-01-27 | A scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106414900A CN106414900A (en) | 2017-02-15 |
| CN106414900B true CN106414900B (en) | 2018-12-28 |
Family
ID=51168215
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580026527.4A Expired - Fee Related CN106414900B (en) | 2014-05-16 | 2015-01-27 | Scroll compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US10294943B2 (en) |
| CN (1) | CN106414900B (en) |
| DE (1) | DE112015002304T5 (en) |
| FR (1) | FR3021075B1 (en) |
| WO (1) | WO2015172895A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102234708B1 (en) * | 2014-08-06 | 2021-04-01 | 엘지전자 주식회사 | compressor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4811471A (en) * | 1987-11-27 | 1989-03-14 | Carrier Corporation | Method of assembling scroll compressors |
| CN101287910A (en) * | 2004-12-22 | 2008-10-15 | 三菱电机株式会社 | Cyclone compressor |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4065279A (en) * | 1976-09-13 | 1977-12-27 | Arthur D. Little, Inc. | Scroll-type apparatus with hydrodynamic thrust bearing |
| US4629403A (en) * | 1985-10-25 | 1986-12-16 | Tecumseh Products Company | Rotary compressor with vane slot pressure groove |
| AU568983B2 (en) * | 1985-10-25 | 1988-01-14 | Tecumseh Products Company | Hermetic compressor |
| JP3050708B2 (en) * | 1992-12-07 | 2000-06-12 | 株式会社日立製作所 | Bearing oil supply device for scroll compressor |
| EP2280148B1 (en) * | 2008-04-07 | 2018-09-12 | Mitsubishi Electric Corporation | Scroll fluid machine |
| US8834139B2 (en) * | 2009-01-30 | 2014-09-16 | Panasonic Corporation | Lubrication of a scroll compressor |
| FR3006387B1 (en) * | 2013-05-31 | 2016-02-19 | Danfoss Commercial Compressors | SPIRAL COMPRESSOR |
-
2014
- 2014-05-16 FR FR1454427A patent/FR3021075B1/en not_active Expired - Fee Related
-
2015
- 2015-01-27 DE DE112015002304.6T patent/DE112015002304T5/en not_active Withdrawn
- 2015-01-27 CN CN201580026527.4A patent/CN106414900B/en not_active Expired - Fee Related
- 2015-01-27 WO PCT/EP2015/051549 patent/WO2015172895A1/en active Application Filing
- 2015-01-27 US US15/310,572 patent/US10294943B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4811471A (en) * | 1987-11-27 | 1989-03-14 | Carrier Corporation | Method of assembling scroll compressors |
| CN101287910A (en) * | 2004-12-22 | 2008-10-15 | 三菱电机株式会社 | Cyclone compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106414900A (en) | 2017-02-15 |
| DE112015002304T5 (en) | 2017-02-09 |
| WO2015172895A1 (en) | 2015-11-19 |
| US10294943B2 (en) | 2019-05-21 |
| FR3021075A1 (en) | 2015-11-20 |
| FR3021075B1 (en) | 2019-06-14 |
| US20170074267A1 (en) | 2017-03-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9879673B2 (en) | Scroll compressor | |
| CN105229308B (en) | Scroll compressor | |
| KR102234708B1 (en) | compressor | |
| EP3372837A1 (en) | Scroll compressor | |
| KR101364025B1 (en) | Scroll compressor with supporting member in axial direction | |
| EP2309132A1 (en) | Horizontal scroll compressor | |
| US10788037B2 (en) | Scroll compressor | |
| JP7075407B2 (en) | Scroll compressor | |
| WO2015104863A1 (en) | Rotary compressor | |
| JP6550645B2 (en) | Scroll compressor | |
| JP6554926B2 (en) | Scroll compressor | |
| WO2016066311A1 (en) | A scroll compressor provided with an orbiting guiding portion for improving the filing of the compression chambers | |
| US9322403B2 (en) | Compressor | |
| US10704549B2 (en) | Screw compressor having a discharging passage with enlarged cross section area | |
| CN106414900B (en) | Scroll compressor | |
| US20110076169A1 (en) | Rotary compressor | |
| KR101447039B1 (en) | Scroll compressor | |
| US10436201B2 (en) | Scroll compressor provided with a lubrication system | |
| EP2884109B1 (en) | Compressor | |
| US20230349381A1 (en) | Fixed Scroll and Scroll Compressor | |
| JP4638313B2 (en) | Hermetic rotary compressor | |
| KR20130011863A (en) | Hermetic compressor | |
| CN101205910A (en) | Scroll compressor having function of reducing lubricating oil resistance | |
| KR101964961B1 (en) | Compressor having structure of gradually changing oil path area | |
| WO2016074817A1 (en) | A scroll compressor including an oldham coupling lubrification system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20181228 Termination date: 20210127 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |